EP2436880B1 - Procédé de modification d`une turbine à vapeur - Google Patents

Procédé de modification d`une turbine à vapeur Download PDF

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Publication number
EP2436880B1
EP2436880B1 EP20110182752 EP11182752A EP2436880B1 EP 2436880 B1 EP2436880 B1 EP 2436880B1 EP 20110182752 EP20110182752 EP 20110182752 EP 11182752 A EP11182752 A EP 11182752A EP 2436880 B1 EP2436880 B1 EP 2436880B1
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EP
European Patent Office
Prior art keywords
maximum thermal
thermal power
blades
steam
fixed blades
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Revoked
Application number
EP20110182752
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German (de)
English (en)
Other versions
EP2436880A1 (fr
Inventor
Fréderic Lamarque
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
General Electric Technology GmbH
Original Assignee
Alstom Technology AG
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Filing date
Publication date
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Application filed by Alstom Technology AG filed Critical Alstom Technology AG
Publication of EP2436880A1 publication Critical patent/EP2436880A1/fr
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Revoked legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/141—Shape, i.e. outer, aerodynamic form
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/80—Repairing, retrofitting or upgrading methods
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y10S415/912—Interchangeable parts to vary pumping capacity or size of pump
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49316—Impeller making
    • Y10T29/49318—Repairing or disassembling

Definitions

  • the present invention consists in a method of modifying a steam turbine, and notably an impulse steam turbine.
  • the method according to the invention makes it possible in particular to adapt the turbine to an increase or a decrease in the maximum thermal power of the steam generator feeding the turbine with steam.
  • a steam turbine is a rotating device intended to convert the thermal energy of steam into mechanical energy for driving an electrical generator, a pump, or any other rotary mechanical receiver.
  • mechanical receiver is meant a mechanically driven device that absorbs power and performs work.
  • the turbine generally includes at least three modules: a high-pressure module, a medium-pressure module, and at least one low-pressure module. Steam supplied by a steam generator is first routed to the high-pressure module and then to the medium-pressure and low-pressure modules.
  • the high-pressure module includes a plurality of stages each provided with a set of fixed blades and a set of moving blades installed on a rotor. Each stage has two functions:
  • a turbine is sized for a maximum thermal power of the steam generator. It may be required to increase this maximum thermal power, for example if it is required to increase the electrical power supplied by the electrical generator driven by the turbine. In this case there is a change from a lower maximum thermal power to a higher maximum thermal power. The turbine must then be adapted to this increased maximum thermal power.
  • the active parts of the turbine are the parts allowing the steam to expand, i.e. the sets of fixed blades and the sets of moving blades attached to the rotor.
  • a second solution consists in anticipating the increase in the maximum thermal power and designing the turbine accordingly, for example by designing the turbine for the higher maximum thermal power and providing means for limiting the steam flow rate to operate at the lower maximum thermal power. Accordingly, in a first variant of this second solution, it is possible to operate at the lower maximum thermal power by limiting the overall steam flow rate by means of steam inlet valves. In a second variant of this solution, it is possible to operate at the lower maximum thermal power by reducing the steam flow rate through one sector of the first set of fixed blades of the high-pressure module.
  • the present invention aims to remedy these drawbacks.
  • the invention proposes in particular a method allowing the turbine to be adapted to the change from a first maximum thermal power - for example a lower maximum thermal power - of the steam generator to a second maximum thermal power - for example a higher maximum thermal power - of the steam generator, with few changes of parts, in a short time period, and preserving a satisfactory efficiency for the two maximum thermal powers.
  • the invention makes it possible in particular to carry out the adaptation of the turbine during the normal maintenance period of a power station, which may be of the order of two weeks.
  • the invention therefore consists in a method of modifying a steam turbine, steam being generated by a steam generator, the method enabling the turbine to be adapted to the change from a first maximum thermal power of the steam generator to a second maximum thermal power of the steam generator, the turbine including a high-pressure module comprising at least one set of fixed blades and a rotor supporting at least one set of moving blades.
  • the method according to the invention comprises the replacement, in the high-pressure module, of at least one set of fixed blades sized for the first maximum thermal power by at least one set of fixed blades sized for the second maximum thermal power. Moreover, the set or sets of moving blades being sized to operate at the first and second maximum thermal powers, the rotor and the set or sets of moving blades of the high-pressure module remain unchanged on changing from the first maximum thermal power to the second maximum thermal power.
  • the set or sets of moving blades may be sized to withstand the mechanical stresses associated with each of the first and second maximum thermal powers and so that, for each stage of the high-pressure module, the combination consisting of the set of moving blades and the set of fixed blades is adapted from a thermo-aerodynamic point of view to the first and second maximum thermal powers.
  • Each set of fixed blades sized for the second maximum thermal power and replacing a set of fixed blades sized for the first maximum thermal power may be a set of fixed blades allowing the passage of a flow of steam a) higher than the replaced set of fixed blades, if the first maximum thermal power is a lower maximum thermal power and the second maximum thermal power is a higher maximum thermal power, or b) lower than the replaced set of fixed blades if the first maximum thermal power is a higher maximum thermal power and the second maximum thermal power is a lower maximum thermal power.
  • each set of fixed blades adapted to the second maximum thermal power replacing a set of fixed blades sized for the first maximum thermal power may comprise blades oriented relative to each other so that the steam flow area between two adjacent blades is a) greater than the steam flow area between two adjacent blades of the replaced set of fixed blades if the first maximum thermal power is a lower maximum thermal power and the second maximum thermal power is a higher maximum thermal power or b) less than the steam flow area between two adjacent blades of the replaced set of fixed blades if the first maximum thermal power is a higher maximum thermal power and the second maximum thermal power is a lower maximum thermal power.
  • the method may be a method of modifying a turbine comprising a medium-pressure module coupled to the high-pressure module, said medium-pressure module comprising at least one set of fixed blades and at least one set of moving blades attached to the rotor of the high-pressure module.
  • the method may further comprise a step consisting in limiting the sum of a) the resultant thrust exerted on the rotor and generated by the pressure differences between the inlet and the outlet of each set of moving blades in the high-pressure module, and b) the resulting thrust exerted on the rotor and generated by the pressure differences between the inlet and the outlet of each set of moving blades in the medium-pressure module.
  • the step of limiting the sum of the resulting thrusts on the rotor may comprise injecting steam onto a thrust surface of the rotor substantially orthogonal to the axis of the rotor.
  • the thrust surface may delimited by a change of rotor diameter.
  • the steam turbine may be an impulse turbine.
  • the second category of steam turbines consists of reaction turbines, in which expansion is divided between the sets of fixed and moving blades. The degree of reaction is defined by the distribution of the expansion between the sets of blades.
  • a steam turbine 1 comprises a high-pressure module 2 combined with a medium-pressure module 3, also called a combined high-pressure/medium-pressure body.
  • the high-pressure module 2 and the medium-pressure module 3 may also be separate.
  • Steam from a steam generator, not shown, passes successively through the high-pressure module 2 and the medium-pressure module 3. Steam thus enters the high-pressure module 2 via an inlet pipe 21 of the high-pressure module 2 and leaves it via an outlet pipe 22. The steam is then directed to the medium-pressure module 3 via an inlet pipe 31 and leaves the medium-pressure module 3 via an outlet pipe 32.
  • the high-pressure module 2 includes a plurality of stages.
  • the high-pressure module 2 comprises nine stages E1 to E9. Any number of stages may be used, however.
  • Each stage comprises a set 2A of fixed blades and a set 2B of moving blades.
  • the sets 2B of moving blades are installed on a rotor 4 and enable the rotor 4 to be driven in rotation by the kinetic energy of the steam that has passed through the sets 2A of fixed blades.
  • Bleed pipes 5 are intended to bleed steam to direct it to a water-heating station which makes it possible to increase the efficiency of the installation.
  • the medium-pressure module 3 comprises a plurality of stages each having a set 3A of fixed blades and a set 3B of moving blades attached to the rotor 4.
  • the medium-pressure module 3 also comprises bleed pipes.
  • the method according to the invention makes it possible to adapt the turbine 1 to the change from a first maximum thermal power of the steam generator to a second maximum thermal power of the steam generator, for example from a lower maximum thermal power to a higher maximum thermal power or vice-versa.
  • a turbine 1 is used in which the sets 2B of moving blades of the high-pressure module 2 are sized to operate either at the first maximum thermal power or at the second maximum thermal power.
  • the sets 2B of moving blades are thus sized:
  • the profiles and the sizes of the set 2A of moving blades are chosen as a function of those of the set 2B [sic] of fixed blades, their sizes and relative disposition having to enable optimum operation of the aforementioned combination whatever the thermal power.
  • the set 2B of moving blades and the set 2A of fixed blades may be sized by controlling in each stage of the turbine 1 the steam enthalpy drop and the degree of reaction, so that the steam enthalpy drop and the degree of reaction satisfy the ranges of adaptation required by the sets of blades for the two maximum thermal powers.
  • an optimum value of the steam enthalpy drop and the degree of reaction there may be taken as the value suited to both powers a function of the two optimum values (for example the mean or other mathematical function).
  • the method according to the invention comprises replacing, in the high-pressure module 2, at least one set 2A of fixed blades so that it is sized, notably by its profile, for the required maximum thermal power, namely the higher maximum thermal power if the turbine was previously operating at a lower maximum thermal power or vice-versa.
  • This replacement is effected in the first stages of the high-pressure module 2.
  • the number of sets 2A of fixed blades to be replaced is a function of the difference between the first maximum thermal power and the second maximum thermal power.
  • the blades of the sets replaced are adjusted.
  • the blades of the sets 2A of fixed blades in question are oriented so as:
  • Figures 2A and 2B show two possible orientations of a set 2A of fixed blades sized for the lower maximum thermal power and figure 2C shows one possible orientation of a set 2A of fixed blades sized for the higher maximum thermal power.
  • the dimensions are given in centimetres.
  • the set 2A of fixed blades adapted to the higher maximum thermal power comprises adjacent blades oriented relative to each other so that the steam flow area between the two blades is larger ( figure 2C ) than the steam flow area between the adjacent blades of the set 2A of fixed blades adapted to the lower maximum thermal power ( figures 2A and 2B ).
  • the pressure differences between the inlets and the outlets of the sets 2B of moving blades in each high-pressure module 2 and low-pressure module 3 generate a resultant thrust on the rotor 4.
  • the sum of these two thrusts must balance, i.e. they must be limited to a threshold value, so as not to damage the rotor 4.
  • FIG 3 which shows a detail from figure 1
  • steam is routed from a bleed pipe 5 (shown in figure 1 ) of the high-pressure module 2 to a thrust surface 6 of the rotor 4 via a pipe 7.
  • the thrust surface 6 is for example located between the high-pressure module 2 and the medium-pressure module 3 in the central part of the body in the case of a combined high-pressure/medium-pressure body.
  • the thrust surface 6 is substantially orthogonal to the axis of the rotor 4 and is located between an area 4a and an area 4b of the rotor 4 delimiting the high-pressure module 2 from the medium-pressure module 3, the area 4b being an area of the rotor 4 of greater diameter than the area 4a.
  • the thrust surface 6 is subjected to the pressure of a bleed from the high-pressure module 2, which makes it possible to limit the resulting thrust on the rotor 4.
  • the steam leaving the pipe 7 is then directed toward a chamber 8 while a chamber 9 collects the steam and limits steam leaks.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Control Of Turbines (AREA)

Claims (8)

  1. Procédé de modification d'une turbine à vapeur (1), la vapeur étant produite par un générateur de vapeur, le procédé permettant que la turbine (1) soit apte au changement d'une première puissance thermique maximale du générateur de vapeur à une deuxième puissance thermique maximale du générateur de vapeur, le procédé comprenant les étapes suivantes:
    - équiper une turbine (1) avec un module haute pression (2) comportant:
    au moins un ensemble (2A) d'aubes fixes dimensionné pour la première puissance thermique maximale;
    au moins un ensemble d'aubes mobiles (2B) dimensionné pour fonctionner à la première et à la deuxième puissances thermiques maximales; et
    un rotor (4),
    - remplacer ledit au moins un ensemble (2A) d'aubes fixes dimensionné pour la première puissance thermique maximale par au moins un ensemble (2A) d'aubes fixes dimensionné pour la deuxième puissance thermique maximale alors que les aubes mobiles (2B) restent inchangées lors du changement de la première puissance thermique maximale à la deuxième puissance thermique maximale.
  2. Procédé selon la revendication 1, caractérisé en ce que l'ensemble ou les ensembles (2B) d'aubes mobiles sont dimensionnés de façon à supporter les contraintes mécaniques associées à la première et à la deuxième puissances thermiques maximales, de telle manière que, pour chaque étage du module haute pression (2), la combinaison constituée de l'ensemble (2B) d'aubes mobiles et de l'ensemble (2A) d'aubes fixes soit adaptée, d'un point de vue thermo-aérodynamique, pour la première et la deuxième puissances thermiques maximales.
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que chaque ensemble (2A) d'aubes fixes dimensionné pour la deuxième puissance thermique maximale et remplaçant un ensemble (2A) d'aubes fixes dimensionné pour la première puissance thermique maximale est un ensemble (2A) d'aubes fixes permettant le passage d'un flux de vapeur a) plus élevé que l'ensemble remplacé (2A) d'aubes fixes si la première puissance thermique maximale est une puissance thermique maximale plus basse et si la deuxième puissance thermique maximale est une puissance thermique maximale plus élevée, ou b) moins élevé que l'ensemble remplacé (2A) d'aubes fixes si la première puissance thermique maximale est une puissance thermique maximale plus élevée et si la deuxième puissance thermique maximale est une puissance thermique maximale plus basse.
  4. Procédé selon l'une quelconque des revendications 1 à 3, caractérisé en ce que chaque ensemble (2A) d'aubes fixes adapté à la deuxième puissance thermique maximale remplaçant un ensemble (2A) d'aubes fixes dimensionné pour la première puissance thermique maximale comprend des aubes orientées l'une par rapport à l'autre de telle manière que la section du flux de vapeur entre deux aubes adjacentes soit a) plus grande que la section du flux de vapeur entre deux aubes adjacentes de l'ensemble remplacé (2A) d'aubes fixes si la première puissance thermique maximale est une puissance thermique maximale plus basse et si la deuxième puissance thermique maximale est une puissance thermique maximale plus élevée ou b) plus petite que la section du flux de vapeur entre deux aubes adjacentes de l'ensemble remplacé (2A) d'aubes fixes si la première puissance thermique maximale est une puissance thermique maximale plus élevée et si la deuxième puissance thermique maximale est une puissance thermique maximale plus basse.
  5. Procédé selon l'une quelconque des revendications 1 à 4, pour modifier une turbine (1) qui comprend un module moyenne pression (3) couplé au module haute pression (2), ledit module moyenne pression (3) comprenant au moins un ensemble (2A) d'aubes fixes et au moins un ensemble (3B) d'aubes mobiles attachées au rotor (4) du module haute pression (2), caractérisé en ce que le procédé comprend en outre une étape consistant à limiter la somme de a) la poussée résultante exercée sur le rotor (4) et produite par les différences de pression entre l'entrée et la sortie de chaque ensemble (3B) d'aubes mobiles dans le module haute pression (2), et b) la poussée résultante exercée sur le rotor (4) et produite par les différences de pression entre l'entrée et la sortie de chaque ensemble (3B) d'aubes mobiles dans le module moyenne pression (3).
  6. Procédé selon la revendication 5, caractérisé en ce que l'étape de limitation de la somme des poussées résultantes sur le rotor (4) comprend l'injection de vapeur sur une surface de poussée (6) du rotor (4) de façon sensiblement perpendiculaire à l'axe du rotor (4).
  7. Procédé selon la revendication 6, caractérisé en ce que la surface de poussée est délimitée par un changement de diamètre du rotor (4).
  8. Procédé selon l'une quelconque des revendications 1 à 7, caractérisé en ce que la turbine à vapeur (1) est une turbine à impulsion.
EP20110182752 2010-09-30 2011-09-26 Procédé de modification d`une turbine à vapeur Revoked EP2436880B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1057947 2010-09-30

Publications (2)

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EP2436880A1 EP2436880A1 (fr) 2012-04-04
EP2436880B1 true EP2436880B1 (fr) 2015-04-22

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ID=43797695

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EP20110182752 Revoked EP2436880B1 (fr) 2010-09-30 2011-09-26 Procédé de modification d`une turbine à vapeur

Country Status (4)

Country Link
US (1) US8821107B2 (fr)
EP (1) EP2436880B1 (fr)
CN (1) CN102444426B (fr)
RU (1) RU2538983C2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6396093B2 (ja) * 2014-06-26 2018-09-26 三菱重工業株式会社 タービン動翼列、タービン段落及び軸流タービン
CN104384814A (zh) * 2014-10-17 2015-03-04 兰州西固热电有限责任公司 一种火电厂汽轮机轴瓦的修复工艺
KR101941807B1 (ko) * 2015-02-10 2019-01-23 미츠비시 히타치 파워 시스템즈 가부시키가이샤 터빈 및 가스 터빈
CN104963728B (zh) * 2015-06-25 2017-07-07 北京全三维能源科技股份有限公司 一种超高压冲动式汽轮机

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GB230114A (en) 1924-03-03 1925-12-31 Bbc Brown Boveri & Cie Arrangement of the dummy piston in steam extraction turbines
FR604508A (fr) 1925-01-06 1926-05-06 Alsacienne Constr Meca Perfectionnement apporté aux aubes mobiles pour turbines à vapeur ou à gaz et autres machines de construction analogue
US3263963A (en) 1964-11-05 1966-08-02 Worthington Corp Nozzle blade assembly comprising replaceable and adjustable nozzle blades
US3356288A (en) 1965-04-07 1967-12-05 Gen Electric Stator adjusting means for axial flow compressors or the like
US4557113A (en) 1984-06-15 1985-12-10 Westinghouse Electric Corp. Single low pressure turbine with zoned condenser
DE3711224A1 (de) 1987-04-03 1988-10-13 Gutehoffnungshuette Man Verstelleinrichtung fuer die leitschaufeln einer axialstroemungsmaschine
US4900230A (en) 1989-04-27 1990-02-13 Westinghouse Electric Corp. Low pressure end blade for a low pressure steam turbine
US4900223A (en) 1989-02-21 1990-02-13 Westinghouse Electric Corp Steam turbine
US4958985A (en) 1989-03-01 1990-09-25 Westinghouse Electric Corp. Performance low pressure end blading
US5056989A (en) * 1990-10-01 1991-10-15 Westinghouse Electric Corp. Stage replacement blade ring flow guide
US5110256A (en) 1991-02-11 1992-05-05 Westinghouse Electric Corp. Methods and apparatus for attaching a flow guide to a steam turbine for retrofit of longer rotational blades
US5292230A (en) 1992-12-16 1994-03-08 Westinghouse Electric Corp. Curvature steam turbine vane airfoil
US5494405A (en) 1995-03-20 1996-02-27 Westinghouse Electric Corporation Method of modifying a steam turbine
US6036433A (en) 1998-06-29 2000-03-14 General Electric Co. Method of balancing thrust loads in steam turbines
DE102007012119A1 (de) 2007-03-13 2008-09-18 Rolls-Royce Deutschland Ltd & Co Kg Drosselgradabhängige Schaufelverstellung bei Strömungsarbeitsmaschinen

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RU2248453C2 (ru) * 1998-08-31 2005-03-20 III Вильям Скотт Роллинс Электростанция и способ получения энергии с комбинированием циклов
ES2278821T3 (es) * 2002-02-06 2007-08-16 Siemens Aktiengesellschaft Turbomaquina con regiones de paletas de alta presion y de baja presion.
US20040170497A1 (en) * 2003-02-27 2004-09-02 Daniel Snyder Beltless high velocity air blower
EP1630359A1 (fr) * 2004-08-23 2006-03-01 Siemens Aktiengesellschaft Turbine à vapeur avec deux chambres à vapeur

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB230114A (en) 1924-03-03 1925-12-31 Bbc Brown Boveri & Cie Arrangement of the dummy piston in steam extraction turbines
FR604508A (fr) 1925-01-06 1926-05-06 Alsacienne Constr Meca Perfectionnement apporté aux aubes mobiles pour turbines à vapeur ou à gaz et autres machines de construction analogue
US3263963A (en) 1964-11-05 1966-08-02 Worthington Corp Nozzle blade assembly comprising replaceable and adjustable nozzle blades
US3356288A (en) 1965-04-07 1967-12-05 Gen Electric Stator adjusting means for axial flow compressors or the like
US4557113A (en) 1984-06-15 1985-12-10 Westinghouse Electric Corp. Single low pressure turbine with zoned condenser
DE3711224A1 (de) 1987-04-03 1988-10-13 Gutehoffnungshuette Man Verstelleinrichtung fuer die leitschaufeln einer axialstroemungsmaschine
US4900223A (en) 1989-02-21 1990-02-13 Westinghouse Electric Corp Steam turbine
US4958985A (en) 1989-03-01 1990-09-25 Westinghouse Electric Corp. Performance low pressure end blading
US4900230A (en) 1989-04-27 1990-02-13 Westinghouse Electric Corp. Low pressure end blade for a low pressure steam turbine
US5056989A (en) * 1990-10-01 1991-10-15 Westinghouse Electric Corp. Stage replacement blade ring flow guide
US5110256A (en) 1991-02-11 1992-05-05 Westinghouse Electric Corp. Methods and apparatus for attaching a flow guide to a steam turbine for retrofit of longer rotational blades
US5292230A (en) 1992-12-16 1994-03-08 Westinghouse Electric Corp. Curvature steam turbine vane airfoil
US5494405A (en) 1995-03-20 1996-02-27 Westinghouse Electric Corporation Method of modifying a steam turbine
US6036433A (en) 1998-06-29 2000-03-14 General Electric Co. Method of balancing thrust loads in steam turbines
DE102007012119A1 (de) 2007-03-13 2008-09-18 Rolls-Royce Deutschland Ltd & Co Kg Drosselgradabhängige Schaufelverstellung bei Strömungsarbeitsmaschinen

Also Published As

Publication number Publication date
CN102444426A (zh) 2012-05-09
EP2436880A1 (fr) 2012-04-04
US20120114492A1 (en) 2012-05-10
CN102444426B (zh) 2015-05-27
RU2538983C2 (ru) 2015-01-10
RU2011113180A (ru) 2012-10-10
US8821107B2 (en) 2014-09-02

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